Horizontal high-speed transfer

ABSTRACT

High-speed transfer apparatus for presses has spaced carrier bars with inward article receiving configurations. The carrier bars are mounted on carrier supports for longitudinal movement therewith and for relative transverse movement with respect thereto. The carrier bars are positively connected to the cam bars for lateral in and out movement therewith and for relative sliding. The carrier supports and cam bars are independently reciprocated in phase displaced relationship so the carrier bar moves forward after the cam bar has moved inward, and so the cam bar draws the carrier outward before the carrier is returned to its first position. The carrier and cam bar are reciprocated by separate rotating cams and followers. A cam flange extends radially outward from a cylindrical body and followers are mounted on opposite sides of the flange for continuous uniform direction rotation of the followers as the cam rotates, and the followers move slides which are connected to the cam bar and carrier bar.

United States Patent [72] inventor Stuart H. McCaughey P.O. Box 255,Cockeysville Road, Cockeysville, Md. 21030 211 Appl. No. 25,725 [22]Filed Apr. 6, 1970 [45] Patented Nov. 16, 1971 Continuation-in-part ofapplication Ser. No. 713,830, Mar. 18, 1968. This application Apr. 6,1970, Ser. No. 25,725

[54] HORIZONTAL HIGH-SPEED TRANSFER 7 Claims, 6 Drawing Figs.

[52] U.S.Cl.. 214/1 [51 Int. Cl 865g 25/04 [50] Field of Search 2l4/ l B[5 6] References Cited UNITED STATES PATENTS 3,430,782 3/l969 Henkel214/1 B FOREIGN PATENTS 597,324 5/1960 Canada 214/] B PrimaryExaminerGerald M. Forlenza Assistant Examiner-George F. AbrahamAt!0rney--Littlepage, Quaintance, Wray & Aisenberg ABSTRACT: High-speedtransfer apparatus for presses has spaced carrier bars with inwardarticle receiving configurations. The carrier bars are mounted oncarrier supports for longitudinal movement therewith and for relativetransverse movement with respect thereto. The carrier bars arepositively connected to the cam bars for lateral in and out movementtherewith and for relative sliding. The carrier supports and cam barsare independently reciprocated in phase displaced relationship so thecarrier bar moves forward after the cam bar has moved inward, and so thecam bar draws the carrier outward before the carrier is returned to itsfirst position. The carrier and cam bar are reciprocated by separaterotating cams and followers. A cam flange extends radially outward froma cylindrical body and followers are mounted on opposite sides of theflange for continuous uniform direction rotation of the followers as thecam rotates, and the followers move slides which are connected to thecam bar and carrier bar.

PAIENTEUunv 1s |97l SHEET 2 BF 6 INVENTOR PATENTEnunv 16 Ian 3.620.381

SHEET 3 BF 6 INVI'INTORS STUART H. McCAUGHEY PATENTEnunv 16 Ian SHEET 6OF 6 INVENTOR STUART H. MOCAUGHEY m @Fm HORIZONTAL HIGH-SPEED TRANSFERBACKGROUND OF THE INVENTION This application is a continuation-in-partof U.S. Pat. application Ser. No. 713,830, filed on Mar. 18, I968, rowPat. No. 3,528,575 by Stuart H. McCaughey for Feed and Transfer Systems.

Very high-speed press operations are made possible by new tool materialsand press designs. One area which has limited the speed of pressoperations is the transfer apparatus which is used to feed articles fromstation to station in presses. Article feed or transfer apparatus hasheretofore employed springs which required excessive operational timesto move a part from one position to another. During the rapidaccelerations while being transfered between work stations, workpieceswhich are not well engaged and held tend to float and misalign, jammingthe machinery, or causing high-rejection rates, and necessitating highpercentages of inspection and sampling. Forces which cause floating andmisalignment increase geometrically with increasing cyclic speeds.

Movements must be very accurate in all transfers. In highspeedtransfers, the accuracy of the transfer movements becomes critical. Playor backlash in transfer apparatus causes many problems which cannot betolerated in high-speed equipment. Because of the increasedaccelerations, many conditions which are completely workable at lowspeeds, become destructive at high speeds. For example, the periodicreversing of direction of a cam follower roller may be tolerated atlowcyclic speeds. When the follower is cycled back and forth at highspeeds, velocities of the roller and cam become high, and braking of theroller against the cam face becomes a serious problem upon each reversalof direction.

SUMMARY OF THE INVENTION The high-speed article feed or transferapparatus described herein is intended to overcome problems associatedwith highspeed transfer operations. The present apparatus is capable ofoperation at 350 cycles per minute and beyond. Each interrelatedmovement is produced by positively interlocked ele ments which permitrelative motion only in the intended directions.

Timing belts are employed to drive the transfer apparatus directly froma rotating shaft which drives the press. A timing belt drives a gearpulley which is attached to a cam drive shaft. Two cylindrical cams arekeyed on the drive shaft with the cams thereon in phased displacedrelationship. In a preferred form, the cams are constructed withradially extended cam flanges which are curved to create the camming orreciprocal motion. Cam follower rollers are positioned on both sides ofthe cam flange so that the rollers continually rotate in a uniformdirection. There is no braking, stopping and reversing direction of thecam follower rollers. The source of wear and backlash is thuseliminated.

The cam flange is preferably constructed with a tapering cross sectionso that its widest dimension is at its base and its smallest dimensionis at its axially outward extremity. Follower rollers are tapered sothat their smallest dimension is nearest the cam drive shaft. Where thecam flanges linear speed is least, it contacts the smallest circle ofthe follower roller. Where the cam flanges linear speed is greatest, itcontacts the largest circle on the follower. Angular speeds of thefollower are constant notwithstanding that the linear speed of the camand follower increase incrementally with the increased distance from thecenter of the cam and drive shaft. Thus, there is no frictional camdrive shaft follower interface, and no backlash is developed.

Slides which support the cam follower axle ride on surfaces which arelubricated by zigzag lubricating channels. Upper surfaces of the slidesare sloped to match the sloping retainer surfaces, which hold the slidesinward toward the drive shaft.

The cam and slide farther from the drive pulley control the forward andrearward motions of the grooved cam bars which move the carriers in andout. The cam and slide nearer the drive pulley reciprocate the carriersupport and carrier bars in which workpiece engaging fingers or groovesare formed. Since the latter apparatus is the heavier of thereciprocating parts, and since it has the longest cyclic movements,acceleration forces are greater than in other parts of the transfer.Consequently, the carrier support and slide connections for the driverod are aligned as closely as is convenient. Angular movements of thedrive rods interconnecting the carrier support and slide are kept to aminimum.

The cam and slide which are further away from the drive pulley aresimilar to the before-described cam and slide. Connecting rods extendforward from the latter slide and connect to the lower flanges of twocranks with parallel vertical axles. Outer ends of the upper flanges ofthe cranks are connected to cam bars. The cam bars drive the parallelcarrier bars in and out between article engaging and disengagingpositions before the carrier bars are advanced or are withdrawn. The cambars are mounted between upper and lower carn slides. In a preferredform of the invention the cam bars have apertures which are angularlyoriented with respect to longitudinal directions of the bars. Sleevebearing mounted wheels are placed within the apertures for rotating onaxles mounted between the slide plates. As the cam bars are reciprocatedlongitudinally, the slope of the apertures causes the cam bars to betranslated at angles to the longitudinal directions.

The carrier bars are attached to the cam bars to permit free relativesliding movement therebetween in longitudinal directions of the bars.The interconnections between the bars prevent relative transversemovement. Consequently, the carrier bars undergo the transversecomponent of the angular movement of the cam bars, while the cam barsslide longitudinally with respect to the carrier bars. The carrier barsmove longitudinally with the cam and slide which are closest the drivepulley and move in and out according to movements of the other cam andslide which are communicated through the cam bars.

The objects of the invention may be carried out with several forms ofcamming means between the fixed frame or slide and the movable cammingbar. For example, cam follower axles might be mounted in the cam barsand angular apertures might be cut in the cam slides.

For accurate longitudinal step by step advancement of the articles andfor maintaining the desired connection between the carrier bars and thecam bars, the present invention provides a reciprocating support onwhich the cam bars are mounted. In a preferred form of the invention,parallel shafts are mounted on the transfer or press frame. The shaftsare mounted at their ends to the frame of the transfer or press.Antifriction ball bearing slides surround portions of the shafts moveback and forth thereon. Carrier supports are mounted on the antifrictionslides, which, with the shafts, insure pure forward and rearwardreciprocation of the supports. Upper surfaces of the supports arebearing surfaces for the carrier bars. The upper surfaces of thesupports are configured for cooperating with the carrier bars to preventforward and rearward movement between the carrier bars and the supportsbut to permit free lateral or transverse movement of the carrier bars.

One object of the invention is the provision of a high-speed horizontaltransfer apparatus with positively controlled interrelated movementsbetween elements.

Another object of this invention is the provision of horizontallymovable transfer carriers and interconnected cam bars.

Another object of the invention is the provision of flanged cams withdouble tapered roller slide interconnections.

These and other objects of the invention will be apparent from thedisclosure which is found in the foregoing and detailed specificationportions as well as in the claims and in the drawings.

BRIEF DESCRIPTION OF THE DRAWINGS cam and follower.

FIG. 5 is a side elevational detail of the carrier bar support.

FIG. 6 is a cross-sectional elevation detail of the carrier bar, carriersupport and cam bar.

DETAILED DESCRIPTION OF THE DRAWINGS Transfer apparatus is generallyindicated by numeral 10 in FIG. 1. A timing belt 12 turns a gear 110 ina direct relation to cyclic operations of a press. Preferably, timingbelt 12 is connected to a press drive shaft which, for example, mayextend outward from an upper portion of a press. Pulley 110 is keyed totransfer drive shaft 108. Also keyed to the drive shaft is a firstcylindrical cam body 120 which has a cam flange 128 radially extendingtherefrom. Cam flange 128 forms a smooth curve with portions of the campositionally varying with respect to an axial direction of drive shaft108. In a preferred form of the cam, thickness at root 126 is greaterthan thickness at radial outward extremity 128. Cam 120 reciprocatesslide 134 by the action of two wheels 130 which are mounted on eitherside of the cam flange 128 and which are connected with axles to slideI34. A second cylindrical body 160 supports a radially extending camflange 164 which drives follower roller 166. The cam follower rollersare mounted on axles 168 which are mounted in slide 170 and which extenddownward therefrom on opposite sides of cam flange 164. Rods 40 havefirst ends connected to pins which extend outward from opposite sides ofslide 170. Forward ends of rods 40 are connected through clevises 44 tocarriers 50 which are schematically represented for clarity as singleelements. Carrier bars 50 have recesses 52 and fingers 54 which griparticles to be transferred step by step between die stations in a press.Rods 40, slide 170 and cam 160 reciprocate the carriers forward andrearward. Inward and outward motion is imparted to carrier bars 50 bycam bars 60. The latter are driven back and forth through linkage whichis moved by slide 134 and cam 120. Rods 62 are connected to a forwardedge of slide 154. Forward ends of the rods are connected to lowerflanges 64 of cranks 66. Upper flanges 68 of the cranks are connectedthrough rod 69 to the cam bars 60.

Each cam bar has several cam apertures 70 which are disposed in the cambar at an angle to a longitudinal direction of the cam bar. Upper andlower cam slides 72 and 74 hold axles on which cam follower wheels 76are mounted. As the cam bars 60 are driven forward and rearward by thelinkage, wheels 76 bear upon the cam apertures 70 causing the bars totranslate angularly in a horizontal plane. As cam bars 60 translate, thetransverse component of the translation is imparted to carriers 50.Elongated hooked shaped interconnections 80 and 82 between the cam barand carrier permit relative longitudinal sliding but prevent relativetransverse motion of the bars. Therefore, carrier bar 50 undergoes thetransverse component of the translation of cam bars 60.

In FIG. 2 the carrier bar 50 and cam bar 60 are shown interconnected andpartially exposed. Rod 40 is connected through a ball joint 90 to a pin92 which is mounted in a support which reciprocates the carrier bar 50longitudinally.

Rods 69 are connected between upper flanges 68 of cranks 66 and clevises94, which are mounted on ends of cam bars 60. Cranks 66 rotate onvertical axles 95.

Upper cam slides 72 hold vertical axles 96 upon which skate wheels 76are mounted. Skate wheels 76 are disposed within cam apertures 70 in cambars 60. As shown in the drawing, the cam bars are in rearward orleftmost position. When the cam bars are moved forward, the angularlyoriented walls of apertures 70 cause the cam bars to move inward. Sincethere are several apertures and skate wheels, the entire bars translateangularly in a forward and inward direction in a horizontal plane. Asthat happens, carrier bars 50 are pushed inward, so that the recesses 52and teeth 54 engage articles 96 in the die stations 98.

Rods 40 are then driven forward, pushing carrier bars 50 and articlesengaged thereby forward to the next die stations. Preferably, thattransfer action occurs as the upper die is being lifted by the press.

On the down stroke of the press, slid 26 moves forward, turning cranks66, and drawing rods 69 and cam bars 60 rearward. The action of skatewheels 76 and cam apertures 70 causes the cam bars to translateoutwardly and rearwardly, drawing the carrier bars 50 outward, anddisengaging the carrier from the articles which remain in the diestations. As soon as the carrier bars have been disengagedfrom thearticles, rods 40 may be rearward, returning the carrier bars 50 totheir original rearward positions.

Referring to FIG. 3, a cam base which is part of the fixed transferframe is configured similar to well-known crankcases. The upper surfaceof the base or frame is a sliding surface with oil groove lubrication.Base 100 is sealed at both ends 102 and 104, where tapered rollerbearings support the shaft for rotation.

One end of drive shaft 108 mounts a gear-toothed pulley which is keyedto the drive shafi. A timing belt drives the pulley 110.

The cylindrical body 122 of a first drive cam is keyed to drive shaft108 at a remote location thereon from the drive pulley. A cam flange 124extends radially from body 122 and smoothly incrementally varies axialposition around the circumference of the body. Cam flange 124 is taperedfrom a maximum cross-sectional dimension adjacent root I26 to a minimumcross-sectional dimension adjacent outer edge I28. Cam follower rollersare mounted on opposite sides of the cam flange. Rollers 130 are taperedcomplimentary to the cam flange taper. Parallel axles 132 extend upwardfrom the cam followers and are mounted in a first slide 134.

As shown in FIG. 4, upper surfaces 136 of the slide body are sloped,whereas lower surfaces 138 are flat. Lower surfaces 138 ride on slidingsurfaces 140 which are lubricated by passageways 142. The sloping uppersurfaces are engaged by complimentary sloping surfaces 144 of retainersI46 which are lubricated by oil passages I48. Rod 62 which drives thecrank and cam bar is connected to a plate secured at the forward end ofslide 134.

A second cam is connected to the drive shaft near the drive pulley. Thesecond cam, cam followers and slide are configured closely similar tothe first cam, and the identification numbers are similar to identifythe elements. One difference between cam 120 and cam 160 is that thelatter has a greater cyclic travel. Cam flange 164 drive cam followerrollers 166. The rollers are mounted on shaft 168 in slide 170. Oilchannels 142 and 148 serve sliding surfaces 140 and 144 as shown in FIG.4. Slide 170 is connected to rod 40 which drives the carrier apparatus.

As shown in the detail of FIG. 5, rod 40 is connected to a clevis whichis mounted on slide support 182. The slid support rests upon anantifriction bearing 184 which surrounds a portion of shaft 186. Shaft186 is mounted at ends thereof with mounts 188 which are anchored on thetransfer or press frame 190.

The slide support 182 is shown in a cross-sectional detail of FIG. 6.Shafis 186 support bearing 184 which surrounds portions of the shaft.The slide support 182 is fixed to the hearing so that support 182 movesforward and rearward or in and out of the drawing plane in purereciprocation. Carrier bar 50 slides on an upper surface I90 of support182. A key 192 and a keyway 194 permit lateral movement of carrier bar50 and support 182 but prevent relative longitudinal movement.

The downward hooked portion 80 of cam bar 60 fits within a groove 196 incarrier bar attachment portion 198. The

hooklike portion 82 of the carrier bar section 198 fits in a similargroove 199 in the cam bar. Thus, the carrier bar 50 and cam bar 60 arepermitted to slide longitudinally relative to each other, but thecarrier bar and cam bar are firmly interconnected to move laterallytogether.

Although the invention has been described with reference to specificembodiments, it will be appreciated by those skilled in the art thatother embodiments may be constructed without departing from theteachings of the invention. The scope of the invention is defined onlyin the following claims.

That which is claimed is:

1. Article transfer apparatus comprising:

a frame,

a cam slide having a horizontal sliding surface fixed to the frame,

an elongated cam bar mounted on the horizontal sliding surface of theslide for movement thereon,

first and second cam means, the first cam means comprising cam aperturesangularly disposed with respect to an elongated direction of the cambar, and the second cam means comprising cam followers positioned in theapertures and having axles extending outward therefrom, one of the cammeans being fixed in the cam bar, and the other of the cam means beingfixed in the frame,

an elongated carrier mounted on the frame parallel to the cam bar andconnected to the cam bar for free relative sliding movement relative tothe frame and for free longitudinal sliding movement relative to the cambar and for lateral movement with the cam bar, the elongated carrierhaving article engaging means on one side thereof,

first reciprocating means connected to the cam bar for moving the cambar forward and rearward in a longitudinal direction thereof, therebycausing angular translational movement of the cam bar by interaction ofthe first and second cam means,

second reciprocating means connected to the carrier for moving thecarrier forward and rearward in a longitudinal direction thereof,

timing means connected to the first and second reciprocating means foroperating the reciprocating means in phasedisplaced relation, wherebythe cam bar and carrier move longitudinally at different times.

2. The transfer apparatus of claim 1 wherein the first cam meansapertures are disposed in the cam bar and wherein the second cam meansfollowers comprise wheels disposed within the apertures and axlesextending outward therefrom and fixed in the cam slide.

3. The transfer apparatus of claim 1 wherein the carrier has at a secondside thereof opposite the article engaging surface an outward and upwardextending elongated portion having a hooklike cross section, and whereinthe cam bar has at a lateral side thereof adjacent the carrier anelongated portion having a complementary hooklike cross section which isinterconnected with the portion of the carrier, permitting relativelongitudinal sliding between the carrier and cam bar, and preventingrelative lateral movement therebetween.

4. The transfer apparatus of claim 1 wherein the carrier mountingcomprises elongated shafts mounted on the frame parallel to the carrierand beneath the carrier, and antifriction bearings surrounding portionsof the shafts, a carrier support fixed to upper portions of thebearings, the carrier support having an upper sliding surface, elongatedcarrier bars mounted on the sliding surface, groove and luginterconnection means on the sliding surface and the carrier bar and theinterconnection means being oriented transverse to an elongateddirection thereof for permitting lateral movement of a carrier bar withrespect to the support and for preventing relative longitudinal motiontherebetween, and wherein a cam bar engaging means is formed on a sideof the carrier bar opposite the article engaging means, and wherein thesecond reciprocating means is connected to the carrier support formoving the support forward and rearward on the shafts and for drivingthe carrier bar forward and rearward with the carrier su rt. I

5. he transfer apparatus of claim 1 wherein the timing means comprises adrive shaft mounted for rotation on the frame, and means for rotatingthe drive shaft, and wherein the first reciprocating means comprises afirst cylindrical body keyed to the drive shaft and having a cam flangeextending radially therefrom at a smoothly varying axial position withrespect to the drive shaft, cam follower rollers mounted on oppositesides of the cam flange, and axles extending upward from the followerrollers, a slide connected to the axles and having a lower surfaceconfigured for sliding on the frame and a linkage interconnecting theslide and the cam bar, and wherein the second reciprocating meanscomprises a second cylindrical body keyed to the drive shaft and asecond radially extending cam flange having smoothly varying axialposition mounted on the second body, second cam follower rollers mountedon opposite sides of the second cam flange, axles extending upward fromthe follower rollers, and a second slide rigidly supporting the axles,the second slide having a lower surface configured for sliding along theframe in a movement controlled by the second cam flange and secondfollower rollers, and second linkage means interconnecting the secondslide carrier.

6. The transfer apparatus of claim 5 wherein the first linkage comprisesa first connecting rod extending from the first slide toward the cambar, a crank having a vertical axis and having a lower radial flangeconnected at an outer end thereof to a second end of the first rod, thecrank having a second flange extending radially outward with an outerend connected to a first end of a second rod having a second endconnected to the cam bar.

7. The transfer apparatus of claim 1 further comprising a second camslide mounted on the frame parallel to the first cam slide, a second cambar mounted on the second cam slide parallel to the first cam bar, thirdand fourth cam means interconnecting the frame and the second cam bar, asecond carrier slidably mounted on the frame parallel to the second cambar and connected thereto for lateral movement therewith, wherein thefirst and second carriers define an article receiving and treating spacetherebetween.

1. Article transfer apparatus comprising: a frame, a cam slide having ahorizontal sliding surface fixed to the frame, an elongated cam barmounted on the horizontal sliding surface of the slide for movementthereon, first and second cam means, the first cam means comprising camapertures angularly disposed with respect to an elongated direction ofthe cam bar, and the second cam means comprising cam followerspositioned in the apertures and having axles extending outwardtherefrom, one of the cam means being fixed in the cam bar, and theother of the cam means being fixed in the frame, an elongated carriermounted on the frame parallel to the cam bar and connected to the cambar for free relative sliding movement relative to the frame and forfree longitudinal sliding movement relative to the cam bar and forlateral movement with the cam bar, the elongated carrier having articleengaging means on one side thereof, first reciprocating means connectedto the cam bar for moving the cam bar forward and rearward in alongitudinal direction thereof, thereby causing angular translationalmovement of the cam bar by interaction of the first and second cammeans, second reciprocating means connected to the carrier for movingthe carrier forward and rearward in a longitudinal direction thereof,timing means connected to the first and second reciprocating means foroperating the reciprocating means in phase-displaced relation, wherebythe cam bar and carrier move longitudinally at different times.
 2. ThetRansfer apparatus of claim 1 wherein the first cam means apertures aredisposed in the cam bar and wherein the second cam means followerscomprise wheels disposed within the apertures and axles extendingoutward therefrom and fixed in the cam slide.
 3. The transfer apparatusof claim 1 wherein the carrier has at a second side thereof opposite thearticle engaging surface an outward and upward extending elongatedportion having a hooklike cross section, and wherein the cam bar has ata lateral side thereof adjacent the carrier an elongated portion havinga complementary hooklike cross section which is interconnected with theportion of the carrier, permitting relative longitudinal sliding betweenthe carrier and cam bar, and preventing relative lateral movementtherebetween.
 4. The transfer apparatus of claim 1 wherein the carriermounting comprises elongated shafts mounted on the frame parallel to thecarrier and beneath the carrier, and antifriction bearings surroundingportions of the shafts, a carrier support fixed to upper portions of thebearings, the carrier support having an upper sliding surface, elongatedcarrier bars mounted on the sliding surface, groove and luginterconnection means on the sliding surface and the carrier bar and theinterconnection means being oriented transverse to an elongateddirection thereof for permitting lateral movement of a carrier bar withrespect to the support and for preventing relative longitudinal motiontherebetween, and wherein a cam bar engaging means is formed on a sideof the carrier bar opposite the article engaging means, and wherein thesecond reciprocating means is connected to the carrier support formoving the support forward and rearward on the shafts and for drivingthe carrier bar forward and rearward with the carrier support.
 5. Thetransfer apparatus of claim 1 wherein the timing means comprises a driveshaft mounted for rotation on the frame, and means for rotating thedrive shaft, and wherein the first reciprocating means comprises a firstcylindrical body keyed to the drive shaft and having a cam flangeextending radially therefrom at a smoothly varying axial position withrespect to the drive shaft, cam follower rollers mounted on oppositesides of the cam flange, and axles extending upward from the followerrollers, a slide connected to the axles and having a lower surfaceconfigured for sliding on the frame and a linkage interconnecting theslide and the cam bar, and wherein the second reciprocating meanscomprises a second cylindrical body keyed to the drive shaft and asecond radially extending cam flange having smoothly varying axialposition mounted on the second body, second cam follower rollers mountedon opposite sides of the second cam flange, axles extending upward fromthe follower rollers, and a second slide rigidly supporting the axles,the second slide having a lower surface configured for sliding along theframe in a movement controlled by the second cam flange and secondfollower rollers, and second linkage means interconnecting the secondslide carrier.
 6. The transfer apparatus of claim 5 wherein the firstlinkage comprises a first connecting rod extending from the first slidetoward the cam bar, a crank having a vertical axis and having a lowerradial flange connected at an outer end thereof to a second end of thefirst rod, the crank having a second flange extending radially outwardwith an outer end connected to a first end of a second rod having asecond end connected to the cam bar.
 7. The transfer apparatus of claim1 further comprising a second cam slide mounted on the frame parallel tothe first cam slide, a second cam bar mounted on the second cam slideparallel to the first cam bar, third and fourth cam meansinterconnecting the frame and the second cam bar, a second carrierslidably mounted on the frame parallel to the second cam bar andconnected thereto for lateral movement therewith, wherein the first andsecond carriers define an article receiving and treating spaCetherebetween.